Gear



H. E. GOLBER GEAR \ Filed June '7. 1939 2 SheetsShee t 1 ATTORNEY,

1941- H. E. GOLBER 2,

- GEAR I Filed June 7, 1959 2 Sheets-Sheet 2 INVENTOR ATTORN mem s Aa q. 19,. 19

UNITED-Q STATE Sf PATENT OF Hyman E. Golber, Chicago, 111., aslignor to Mickie Printin Press and Manufactnrin clum lli., a corporation of Illinois I i'lo i uumr.

Application June 7, 1839', Serial No. 277,858

14 Claims. ((174-437) complementary, roll-curve gears, and it con--- cerns more particularly pairs of intermeshing gears'which provide a non-uniform or varying rotation, at least in part, of the driven gearof the couple.

One aim of the invention is to supply gears capable of affording movements of mechanical elements which heretofore have been impossible or impractical to make, and, by reason of this invention, the motions capable of production are now of the greatest variety.

Another object of the invention is thesupplying of gears ofthis character which are free from curves. and (d) the production of the novel driving and driven gears under the control of such dominant patterns or cams.

cusps and which have all of their teeth in a sin I gle plane, or at least in operative register.

A. further purpose of the invention lathe making of roll-curve gears which will give the least degree of shock to the parts involved, even though the driven-gear and its associated mechanical-elements are operated at variable speeds. a In automatic machinery, the movements of the various parts thereof are usually obtained from the motion of a follower impelled or actuated by a driver, the latter ordinarily rotating at a uniform speed, the follo'werhaving some definite motion, usually one of rotation. when the follower motion .is a rotation at uniform speed, the driver and follower are customarilyconnected by ordinary circular gears; when the follower .motion is a rotation of non-uniform speed, irregular-shaped gears are sometimes used: and when the follower moves in a more complicated manner, various kinds of devices, such as cams, planetary-gears, levers, or sundry combinations thereof are used. Frequently, the designerof the machine is unacquainted with any means which will produce the required follower motion, and, therefore. he is compelled to resort to an undesired motion which he knows how to produce.

' Accordingly, the outstanding problem to be solved by the present invention was the production of gears of such characteristics as to make it possible to give to the follower or drivengear practically any desired motion, and the novel features of this invention enables a designer to effect the follower motion wanted, and, consequently, to obtain the most excellent condition in the machine which he is devising.

Stated in a general way, the production of the gears incorporating the instant invention involves (a) the development of a speedgraph of the follower or driven-gear from data of the required, at least in part, non-uniform motion, (b) the development of roll-curves for' both the driving and driven gears, (c) the making of master-patterns in accordance with such roll- The invention can best be understood by ref-.

erence-to the illustrations in the accompanying drawings in which- Figure 1 illustrates an original anda modified so-called speedgraph;

Figure 2 portrays the pair of roll-curve gears produced;

Figure 3 shows the method of making the first, reduced-size master-cam for the driven-gear;

Figure 4 presents the same for the drivinggear; v

Figure 5 depicts the complete, first mastercam for the driven-gear:

Figure 6 pictures the same for the driving- E Y v a Figure 7 discloses the second, full-size, rollcurve master-cam for the driven-gear: and

Figure 8 sets forth the same for the drivinggear.

It is to be understood, of course, that in pre-' senting an example of how the invention may be put into commercial practice, no statement contained therein should be deemed as constituting any limitation on the scope of the invention as defined by the'appended claims.

To facilitate an understanding of this inven tion and to indicate the differences between more or less related terms, the following definitions should be kept in mind: acceleration is the rate of increase of speed, deceleration is the rate of decrease of speed, displacement is the change of position with the element of time omitted, speed is the rate of change of displacement, and impulse is the rate of change of acceleration or detime at least, is variable in order to produce required non-uniform movements.

Accordingly, using a rectilinear-system of coordinates, a speedgraph line is drawn representing the needed speedcharacteristics of the driven-gear to be provided, and in Figure. lsuch a line is shown partlyin full line and partly dotted.

In such Figure 1, the horizontal base-line Hitllt JZlL- Ht-Hll-lliO-lttlllll8ll- Hill represents zero speed, distances above such baseline delineating follower or driven gear rotation in the opposite direction to that of the drivinggear and distances below such base-line denot- I ing driven-gear rotation in the same direction as that of the driving-gear.

plots the required speedrotation of the follower or driven gear to be supplied, the line l10l00-- I20 portraying a period of dwell or non-rotation oi the follower-gear, the two ends of the line characterized I00, I representing the same single point; that is to say, the follower does not rotate for the period represented by the space liii-i'ilt-HG.

That straight portion l20-i9 of the line indicates a uniform acceleration of rotation of the follower-gear, in other Words, a parabolic angular-displacement of the gear around its axis; that horizontal part lit-2i of the line designates a uniform rotation of the follower or driven gear at the highest speed reached at the end of the acceleration; and that straight section 2l-i10 of the line depicts a uniform deceleration or parabolic decrease of angular-displacement of the rotating follower-gear.

In drawing such a speedgraph, any unit of length is arbitrarily chosen to represent the known uniform rotational speed of the drivinggear, and the vertical speed-ordinates of the follower-gear line of the speedgraph are of lengths based upon such unit .of length, the latter being showninFlgure 1 as line -22. g

It is to be particularly noted that in this speedgraph the periods of parabolic angular-displacement of the driven-gear are not denoted by curved or parabolic lines, but rather by-straight inclined or sloping lines nil-I8 and i l-Illindicative of uniform change of speed. I The point l9, therefore, depicts a sudden ter mination of the constant substantial acceleration of the follower-gear and an abrupt institutionof its uniform speed of rotation, which gnore or less violent transition, if it were allowed to occur, would create a shock in the mechanism with resulting detrimental effect, especially in a machine requiring great accuracy in the movements of its parts, as, for example, in a printing-press where registration of printing or positioning of sheets of paper are of prime importance.

The point 2| represents a similar but reverse shock-creating condition, that is to say, the quick ending of its uniform-speed revolution and the instant establishment of its period of its uniform deceleration at a material rate.

It is to be understood further that the area beneath the line Mil-l9, or iii-2|, or 2i-l10 represents the angular-displacement of the follower-gear, and this, of course, is true of any portions of such lines, the total area i-l92i- I'm-I20 corresponding to 360 degrees of rotation of the follower-gear.

To avoid such abrupt or quick changes of rotation of the follower or driven gear, portrayed by the cusps at l9 and 2|, it becomes desirable or necessary to eliminate these cusps by the substitution of curves therefor, but, inasmuch as the areas below such curves must be dealt with in the development of the roll-curve for the drivengear, it is of great importance that the curves chosen shall be such as (a) to facilitate or even make possible the ready ascertainment of the whole or partial area below the complete curve or section thereof, and (b) to be consonant or compatible with the functioning capacity of available gear-tooth cutting-machines.

I have discovered that the best curve to employ for this purpose, and for the accomplishment of the above-stated and other objects, is a parabola with its axis at right-angles to the horizontal base-line, such curve providing a constant rotational impulse to the follower-gear.

Such parabola should be preferably relatively large, rather than small, in order to afford smooth action of the gears, and to aid in the cutting of the gear-teeth, and it may be readily computed and drawn, requiring no reference to trigonometric tables.

The parabola so selected may depend somewhat upon the desired requirements in the finished machine, bearing in mind that the companion driving-gear must cooperate with the final follower or driven gear at, these points, and remembering the facilities available for cutting the gear-teeth, etc., but no difficulty will be experienced by one in providing such cusp-elimibe tangent to both of the lines which it connects, thus assuring no drastic or undue changes of acceleration of the follower-gear.

In Figure 1 the speedgraphvhas been modified to indicate the employment of parts of two su'itable parabolas to remove the cusps referred to, and, in such figure, the parabolic lines III-l4 and iB-IG have been introduced to take the place of the upper portions of the lines -19 and fig-g0 and the opposite end portions of the line In the final speedgraph chart, it is to be remembered that the ordinates of the curve represent speed, the area beneath the curve angulardisplacement, and the grades of the curve acceleration or deceleration, as the case may be.

From this new altered speedgraph curve or line IOU-Iill--l3l4-l5-l6l8lll00, and in which the ordinates "-440 and l5-l5 represent the axes of the two parabolas, it will be seen that the constant acceleration or parabolic angular-displacement, indicated by the straight, sloping line lit-i3, is gradually and smoothly modified, as represented by the parabolic line Iii-i4, so that, although acceleration continues line ll-Ii.

Again, such uniform rotational speed of the driven or follower gear is ended at the point I! and deceleration thereof instituted gradually and smoothly and then more or less rapidly increased,

a as represented by the parabola section li-i 6, and

at the point It, such deceleration becomes and continues constant and unvarying until the be ginning of the dwell at the point I80.

It should be observed'that ateach of the points l3, ll, i5 and IS the parabolas are tangent to the tion'of the parts actuatedby the driven or follower gear and that the rapidity of acceleration and deceleration, as represented by the lines 0-19 and 2I-il0, may be slightly changed without interfering with the successful operation of the machine.

To produce this result, the section of the parabola it-H is introduced into the speedgraph withthe vertex of the parabola at the point It, and the slope of line "ll-l9 is decreased slight- 1y. so that the parabola is tangent to the line Hl-W and also tangent to the new line Ila-II, the inclination of line |20-IQ having been changed Just enough so that the area I l--i 3-I 4-4 40-1 30--l l0, representing angular-displacement of the driven-gear, in the final speedgraph, is exactly the same as the original area l 20-l9-H-H0-l30-l20.

As is fully shown, this change of inclination is brought about by shifting the intersection of line l9--l 20 with the base-line atthe point I20 slightly to the left to point H0 and terminating the new straight inclined line at the point ll.

As will be readily understood, another section of parabola |;il6 is similarly introduced into the diagram to eradicate the cusp at 2|.

If it were essential to maintain the length of line l9--2| to secure a predetermined period of constant speed of the driven-gear and it were permissible to change the period of, or'rate of,

One acquainted with, and skilled in, this art will encounter no substantial dimculties in removing the cusps by the adoption and introduction of the parabolas and at the same time preserving the required irregular rotation of the follower-gear to be produced.

In every instance, the parabola employed has its axis vertical, that is at right-angles to the base-line, to facilitate mathematical calculation, rather than resorting to complicated formulae or trigonometric tables.

Actually, in this speedgraph chart of Figure 1, the total angular-displacement of the driving- 7 gear should be represented by the area of a Hill-4 l|l= 29.6388885 degrees ill-Ill: 40.0000000 degrees [MI-440: 40.0000000 degrees 0-! III= 14037222230 degrees l 5lll 6fi= 40.0000000 degrees l60l80= 40.0000000 degrees Nil-I00: 29.6388885 degrees The illustrated vertical ordinates of the follower-gear curve of Figure 1 are as follows and their values show their proportion of the unitspeed ordinate loll-22 of thedriving-gear:

"0-4 3:1.00628931 Ill-l 4 1,50943 396 Iii-4 5:1.50943396 1"li=1.00628931 v As the line portion lBli-lOlJ-i ill is a dwell for the driven-gear, point 30 (Figure 2) on the dotted extension of the roll-curve of the latter would Moreover, the gear portions on line ll-43' near the point H0 and on line lfi-ISO" near the point I" are not satisfactory because the gears would unmesh, and so the cam-and-roller drive is made to provide also for the disadvantageous lower portions only of lines il0i3 and I6--l80.

It has been indicated previously that the cusps are to be removed from the speedgraph and yet two remain at H0 and IE0, these two occurring, not on the gear-portion, but on the cam-portion, as Just stated above, when the follower-gear speed is very low; yet in some speedgraphs even the speed-'zero cusps are rounded out.

The manner in which such'cams and rollers may be employed for the specified purpose is fully presented in my United States Patent 2,027,818,

Drive-mechanism, granted January 14, 1936 and need not be referred to here further.

Now for each degree of turn of the drivinggear beginning at zero at the point I00 (lefthand end of the line), for each corresponding ordinate of the followerw-gear curve l00ll0- tcrmining such areas under each parabola,'onestarts with the axis (ll-I40 or l5--l50) of the parabola and works backwardly for the parabola l3 and forwardly for the parabola li-llas otherwise the computation would perhaps be unduly complex.

For example, the driven-gear does not begin to rotate until the driving-gear has turned 29.6388883 degrees corresponding to the point H0, and, while the driving-gear revolves the next 40 degrees, as represented by that portion of the base line 0-130, the driven-gear. must rotate an amount corresponding to the area is determined in this HII3I30 which manner:

In this connection it must be appreciated that, although the length of line Iii-l3 is greater than the length of the line lit- I30, neverthe less the driven-gear is rotated" a lesser amount during the rotation of the driving-gear than that of such driving-gear, this being due to the fact that whereas the length of line ll-I30, as we are now considering it, represents the extent of rotation of the driving-gear, the area beneath line I l0 -l 3 represents the rotation of the drivengear during the same period.

If, however, we were comparing the actual area of the driving-gear rectangle having a base lib-Ill and a height loll-22 with that of the driven-gear triangle ll0-I30--|3 the relative angular-displacements of the two gears during the same period of time would be more obvious.

The line III-H0 depicts a turning of the driving-gear of 40 degrees, and, during such rotation thereof, the driven-gear will be revolved an amount corresponding to the area ll0-l3--' It-HI), which is computed in known manner thus:

1 -14 140= Am 130- 13 140 1a0-13 +2(14o 14 A 1ao--13-14 m 40 degrees x (1.00628931 2(1.50943396) the driven or follower gear revolves 53.66876305- degrees, and, while the driving-gear thereafter turn 29.6388885 degrees, denoted by line ISO-I80. 20.1257862 degrees.

By this time, the driven-gear has completed its single 360 degree revolution, and it dwells or remains stationary during the period the driving-gear turns two times 29.6388885 degrees, that is 59.2777770 degrees, represented by the combined lines I80 lIi0--IIII.

As will be readily understood, the area beneath the straight sloping line Ii-I3 represents a uniform acceleration of the driven-gear, the area beneath the section I3-I4 of the vertical parabola corresponds to a constant impulse resulting in a graduated reduction of the acceleration, whereby the rotation of the driven gear reaches a uniform onunvarying speed at the point M, which condition persists, as represented by the rectangle IlIl-Il-Ili-ISO, until point I5 is reached, whereupon the speed of the driven-gear is decelerated at a gradually increasing rate which at the point It becomes a uniform deceleration until point I80 is reached, where such deceleration has brought the driven-gear to-a standstill.

Machines are assumed to be'built of rigid material, as for example, cast-iron, but, of course, in reality there is no such thing as an absolutely rigid material, that is every body bends in some degree when forces are applied to it, the amount of bending being proportional to the stress to which it is subjected.

Since in a -machine, the inertia forces are proportional to the square of the machine-speed, such bends of its parts created by such forces are proportional to the square of the machine-speed times acceleration.

At every speedgraph cusp, the bodies would have two diiferent bendings corresponding to the different grades of the lines meeting at the cusp, and, since it frequently happens-that the bodies are considerably resilient, they would bend sufficiently to cause misplacement of the parts, and, at high speed, would knock and result in defective operation of the mechanism.

Such troubles are'eliminated by the practice of the present invention based on the removal or avoidance of cusps in the speedgraph curve.

The following table may be of assistance in I analyzing what happens to the driven-gear at different parts of the speedgraph-chart:

the companion driven-gear turns In Figure 2, the driving-gear 3| and its attendant or mating follower or driven gear 32 are shown in meshed relation, in this particular or specific example with a fixed distance of 16.625 inchesbetween their axes 33 and 34 respectively about which they are designed to revolve.

We will now consider the manner in which such pair of gears is produced from the speedgraph of Figure 1.

For each degree of rotation of the drivinggear, as indicated by the line IOU-I00, the cor responding amount of turning of the drivengear is determined mathematically in the same general manner as indicated above for the particular points H0, I30, I40, I50, I80, I80, so that for each added degree of turning of the drivinggear, from its starting point, the total amount of turning of the driven- -gear will be known.

It can be readily demonstrated that with these roll-curve gears, the ray (not radius) (R for the be written thus:

. 1+s and similarly the equation for the ray of the driven or follower gear may be expressed thus:

- +5 The roll-curve for the driving-gear may be plotted on a sheet of paper by drawing 360 rays from a common center one degree apart and marking on each such ray line the proper length thereof as determined by the above-noted formula, and then by drawing a line through all or the rays may vary as to the degrees or angle between them as determined for each degree of turning of the driving-gear and the marks applied to such rays.

In either case, a line drawn through the successive marks or points results in the drivengear roll-curve.

Instead of using rays for the location of such roll-curve points, a system of rectilinear-coordinates may be resorted to.

Bpeodgraph Displacement Speed Acceleration Impulse ,Horizontelzeroline 0... 0 0 0. Horizontalupperlino.. Changes at uniform Remains coustant 0 0.

re Oblique straight'llnes... Parabollc chaieges at uniform Remains constant..-... 0.

' ra Parabolas Cubic Parabolic Changes at uniform Remains constant,

rate.

aacaa'ro Such driving-gear roll-curve 35 (Fig. 4) may be originally plotted and drawn on the plane face of a fiat metal plate 35 of suitable thickness, or may be transferred thereto from the curveplotted on paper, and, in like manner, the driven-gear rollcurve 31 (Fig. 3) may be plotted on another suitable blank plate 38.

Each such plate then has its center portion cut out by providing a series of overlapping holes through the plate by a rotary-cutter, the axis or center of which in each cutting operation is in register with the corresponding roll-curve, and, a hole is thus cut'through the plate for each of the equally-spaced (one degree) rays of the driving-gear roll-curve and for each of the rays for the roll-curve of the driven-gear.

Some only of such holes 39 are shown for the driving-gear and these are not spaced as close to one another as in actual practice, corresponding holes 4I being used in the other plate 33.

' After all'of these holes have been cut we have a crude first master-cam 42 for the driving-gear and a similar first master-cam 43 for the drivengear, each cam being smaller all around by the radius of the cutter than the corresponding rollcurve, alias is clearly shown.

To preclude any relative movement of each such cam and the blank from which it is being cut in the manner indicated, the blank should initially-be fastened fixedly at several points to a sustaining or supporting plate or member whereby each cam 42 or 43 is immovable with re- .latlon to its blank 36 or 38 during the entire cam cam 42, 43 will have minor transverse ribs or ridges on its edge and these are very carefully removed by filing or grinding, thus providing the final first master-cams I42 and I43.

By using these first master-cams with rollers traveling on their edges and with suitable mechanically-associated cutters, the. positions of which are controlled by the shapes of such first cams, and by means well understood by any machinist, second full-size roll-curve master-cams 242 and 243 are provided and these have periph-.

cries exactly like the corresponding roll-curves 35 and 31.

The reason why such final full-size cams 242 and 243 cannot be made direct by the method oi! producing the first cams I42, I43 isthat the rays 01' the roll-curves are not always normal to the curves.

As a matter of fact, while it is ordinarily de .sirable to do so, it is not essential and imperative that the roll-curves 35 and 31 be produced, either on paper or on the metal blanks from which the first master-cams are made, but rather the successive points for the location of the center or axis of the cutter may be selected and obtained on an accurate machine, working on a rectilinearsystem of coordinates for placing the cutter in its series of positions relative to the blank on which it operates.

For example, assume that the axis of the rotary-cutter is fixed, then the blank is capable of two definite movements at right-angles to one another for locating the cutter with great exactitude for producing the required hole through the blank orcut from the, edge of the blank, and,

then for the next hole or cut, the blank fixedly mounted on the movable or adjustable member of the machine is shifted by adjustment of such member into correct position for the next hole such cutting in which the metal-blank remains stationary and the cutter is adjusted in two directions at right-angles to-one another.

The two, second, full-size master-cams 242 and 243, having been made in the manner indicated, it .now becomes necessary to make a pair of roll curve gears 3I and 32 under their control.

Using these two cams, similar gear blanks are made, the shapes thereof being governedby rollers traveling on the edges of the two cams, but such rollers and the cutters controlled thereby are so related that the gear-blanks have addenda to provide for the gear-teeth to be subsequently out.

. Assume that master-cam 242 is slowly revolved about its axis 244 and that a roller of proper size is held against its cam periphery under great pressureto preclude slipping, and assume that such roller is also mechanically connected to and revolves a rotary gear-tooth -cutter,.such as is commonly employed in a Fellows gear-cutting machine, acting on the corresponding gear-blank referred to, such gear-tooth cutter cuts the teeth on the blank, the number of teeth and pitch having been determined in accordance with the standard practice in making ordinary spur-gears.

In this case, such master-cam, through its associated roller, revolves the gear-tooth cutter on its axis for the cutting of the teeth, the moving of such cutter in and out toward and from the axis of the gear-blank being also produced by such master-camthrough such roller. The moving of the gear-tooth cutter to clear the gearblank on the return stroke of the cutter is provided as in a Fellows gear-tooth cutting machine.'

In this manner, the first driving-gear 3I ismade, and, in an analogous way, the initialdriv en-gear 32 is supplied while the master-cam243 revolves around its axis 245.

Inv the cutting of the teeth of subsequent gears on theirblanks. the corresponding master cani 242, in. the case of the making of the driving I gear, controls the in-and out (not return-clean ance) travel of. the ear-tooth cutter,"but, by

' having the first gear. 3| rotate simultaneously about its axis and gearing it to the gear-tooth cutter, a positive rotation of the latter occurs,.

rather than through the friction-drive employed in making the first gear, and, of course, it will be understood that the subsequent driven-gears will be made in an, analogous manner. 4

Those acquainted with this art will readily understand that the specified objects and aims of the invention are attained by practicing the procedure herein set forth and in the resulting cooperating roll-curve gears produced in this way.

The method of making the roll-curve gears disclosed above constitutes the subject-matter of my co-pending patent application, Method of making gears, Serial No. 310,502, filed December I claim:

1. A pair of complementary driving and driven gears having roll-curves shaped, when the gears are intermeshed and the driving-gear is rotated about its axis in a predetermined manner, to angularly revolve the driven-gear about its axis. for at least a part'of its complete revolution, at a constant rate of change of acceleration, the toothed edge of each gear being free from cusps.

2. The pair of gears set forth in claim 1 in which the stated revolution of the driven-gear is produced when the driving-gear is rotated about its axis at a uniform speed.

80 3. A pair of complementary driving and driven Bears having roll-curves shaped, when the gears are intermeshed and the driving-gear is rotated about its axis in a predetermined manner, to angularly revolve the driven-gear about its axis, for at least a part of its complete revolution, at a constant rate of change of deceleration, the toothed edge of each gear being free from cusps.

4. The pair of gears set forth in claim 3 in which the stated revolution of the driven-gear is produced when the driving-gear is rotated about its axis at a uniform speed. I

5. A pair of complementary driving and driven gears having roll-curves shaped, when the gears are intermeshed and the driving gear i rotated about its axis in a predetermined manner, to angularly revolve the driven-gear about its axis, for at least a part of its complete revolution, at a constant rate of change of decrease in acceleration and at a constant rate of change of increase in deceleration, the toothed edge of each gear being free from cusps.

6. The pair of gears set forth in claim- 5 in which the stated-revolution of the driven-gear is produced when the driving-gear is rotated about its axis at a uniform speed.

'7. A pair of complementary driving and driven .gears having roll-curves shaped, when the gears tion, then at a constant speed of revolution, and then at a constant rate of change of increase in deceleration, the toothed edgeuf each gear being free from cusps.

8. A pair of complementary driving and driven gears having roll-curves shaped, when the gears are intermeshed and the driving-gear is rotated about its axis at a uniform speed, to angularly revolve the driven-gear about its axis. for at least a partof its complete revolution, at a constant rate of change of decrease in acceleration, then at a constant speed of revolution, and then at a constant rate of change of increase in deceleration, the toothed edge of each ge'ar being free from cusps and with all of its teeth in operative register around such edge.

9. A pair of complementary driving and driven gears having roll-curves shaped, when the gears are intermeshed and the driving-gear is rotated about its axis in a predetermined manner, to angularly revolve the driven-gear about its axis. for at least a part of its complete revolution, at a constant acceleration, then at a uniformlydecreasing acceleration, then at a uniform speed of revolution, then at a uniformly-increasing deceleration, and then at a constant deceleration, the toothed edge of each gear being free from cusps and with all of its teeth in operative register aroundsuch edge.

10. The pair of gears set forth in claim 9 in which the stated revolution of the driven-gear is produced when the driving-gear is rotated about its axis at a uniform speed.

11. A pair of complementary driving and driven gears having roll-curve shaped, when the gears are intermeshed and the driving-gear is rotated about its axis in a predetermined man- "ner, to angularly revolve the driven-gear about its axis, for at least a part of its complete revoluare intermeshed and the driving-gear is rotated.

tion, at different speeds and at a speed, between said periods of different speeds, corresponding to the progressively-varying area of a zone bor-' dered on at least one side by a portion of a parabola, the toothed edge of each gear being free from cusps.

12. The gears set forth in claim 11 in which the driven-gear has the speed characteristics specified when the driving-gear is rotated about its axis at a uniform speed.

13. The pair of gears set forth in claim 11 in which said zone has two parallel sides, in which the axis of the parabola is parallel to said sides, and in which said area varies progressively in a direction at right-angles to said axis.

14. The pair of gears set forth in claim 11 in which the driven-gear has the speed characteristics specified when the driving-gear is rotated about its axis at a uniform speed, in which said zone has two parallel sides, in which the axis of the parabola is parallel to said sides, and in which said area varies progressively in a direction at right-angles to said axis.

HYMAN E. GOLBER. 

